High speed can printing press



1956 I w. E. BRIGHAM ETAL 3,227,

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 1 INVENTORS Mew 5 586 /64/ 1 gy/beaerz. faezer QaesvaKA/wfixa:

1 M] W. mm

Jan. 4, 1966 Filed Sept. 4, 1964 W. E. BRIGHAM ETAL HIGH SPEED CAN PRINTING PRESS 16 Sheets-Sheet 2 IN VEN TORJ ArrazA/IYS Jan. 4, 1966 w. E. BRIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS- Filed Sept. 4, 1964 16 Sheets-Sheet 5 W. E. BRIGHAM ETAL HIGH SPEED CAN PRINTING PRESS Jan. 4, 1966 16 Sheets-Sheet 4 Filed Sept. 4, 1964 Ma 15'. 5,8/6HHM r m 2L N mwfl Zh 45 7: in if U az 3% a B .m

Jan. 4, 1966 y w. E. BRYIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 5 1966 w. E. BRIGHAM ETAL 3,

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 6 INVENTORS M20 5 Zea/fix ayfiaaerz. tbetzer ages/v65 K/V/ibwm Jan. 4, 1966 w. E. BRIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS 16 Sheets-Sheet 7 Filed Sept. 4, 1964 Jan. 4, 1966 w. E. BRIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 8 INVENTORS M420 JZ/V/M y flaferl. [axe/er I w. E. BRIGHAM ETAL 3,227,070 HIGH SPEED CAN PRINTING PRESS Jan. 4, 1966 16 Sheets-Sheet 9 Filed Sept. 4, 1964 Jan. 4, 1966 w. E. BRIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 10 ATTORNEY Jan. 4, 1966 w, E BRIHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 11 Jam 1966 w. E. BRIVGHAM ETAL 3,

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 12 39/ @Obed L.Eci(er- 390/ 4 CIArence K mflcffenzle 25M) M 4 MMQ Jan. 4, 1966 w. E BRIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS 16 Sheets-Sheet 15 Filed Sept. 4, 1964 Jan. 4, 1966 w. E. BRIGHAM ETAL 3,

HIGH SPEED CAN PRINTING PRESS Filed Sept. 4, 1964 16 Sheets-Sheet 14 HIIIIIHHHHI INVENTQR BY fluixi sdm q (3PM ATTORNEY l w. E. BRIGHAM ETAL 3,227,070

HIGH SPEED CAN PRINTING PRESS Jan. 4, 1966 16 Sheets-Sheet 15 Filed Sept. 4, 1964 Gm BM MN wfi mm 9. i mwm r m v mwm N E 4/ MB wmm Sm ATTORNEY Jan. 4, 1966 Filed Sept. 4, 1964 W. E. BRIGHAM ETAL HIGH SPEED CAN PRINTING PRESS 16 Sheets-Sheet 16 g QW SM M United States Patent 3,227,070 HHGH SPEED CAN PRINTING PRESS Ward E. Brigham, 250 Springfield Ave, Rutherford, NJ;

Robert L. Eckert, 7 Stephens Ave., Lincoln Park, N.J.; and Clarence K. Maclienzie, 85 Montross Ave, Rutherford NJ.

Filed Sept. 4, 1964, Ser. No. 395,113

laims. (Cl. NFL- iii) This is a continuation-in-part of our prior application, Serial Number 56,437, filed September 16, 1960, now abandoned.

This invention relates to a machine for printing, coating or otherwise decorating the exterior surface of a cylindrical container, and is particularly directed to apparatus which performs these functions at very high speeds.

It ha been, for many years, the objective of workers in the cylindrical container printing art to develop a machine which could accurately decorate containers of this type at high speeds. In the development of machines of this class there are many problems which must be solved. The can making industry is constantly developing thinner and lighter containers, particularly in the plastic and aluminum fields, which are difficult to handle at high speeds due to their relative lightness and thinness. Therefore, it is a particularly important objective of this invention to provide a container printing machine capable of printing cans in excess of 200 per minute.

The can making industry also is constantly developing new and varied sizes and shapes for containers. This invention provides structure adaptable for printing many sizes and shapes of such containers.

Still further the invention provides, as one of its objectives, a novel means to feed cans from a source of supply to the can handling assembly. This objective is obtained partially through the use of trough-shaped cups with air pressure positively positioning the cans therein.

Another important objective of the invention is the structure embodying the means by which the container feeding and handling apparatus is smoothly moved into and out of its normal operating position.

The invention utilizes a disc having container carrying spindles about its surface to present the containers to the printing cylinder. An objective of this invention is the provision of a novel spindle which permits the rapid acceptance, rejection, or removal of a container.

Another important objective of this invention is to provide a container feeding and handling apparatus which is separably mounted with respect to a printing assembly, such that the entire container handling and feeding apparatus is immediately thrown out of contact with the printing assembly when a malfunction or no-can condition is detected. This objective, in the embodiment described, is obtained by mounting the heavy container feeding apparatus on rails so that an eccentric mechanism, having a great mechanical advantage ratio, may disengage and return the two assemblies in several tenth of a second. As a result, minor malfunctions do not interrupt the coating and printing procedures.

In high speed handling apparatus of the type disclosed, there are many coordinated fast moving parts traveling at different speeds, and still other parts that are coordinated therewith but move intermittently. This invention has as one of its objectives the attainment of such coordination through the use of a common drive to obtain all movements.

For commercial consideration, it is necessary for machines of this type to be capable of printing containers having various diameters and lengths. It is, therefore, a still further objective of this invention to provide an assembly wherein the can handling apparatus with respect to the printing cylinder is adjustable longitudinally for can size, and pivotally to obtain uniform printing along the outer walls of the cylindrical containers. This objective is obtained without disturbing the common drive apparatus mentioned in the previous paragraph.

Another important objective of this invention is to provide novel vacuum and pressure type air handling aids so that containers of very thin and light construction may be conveniently handled, transferred and positioned at high speeds.

The high speed handling procedures become especially difiicult after the entire outer cylindrical surface has been coated, or printed. This invention provides air vacuum and pressure takeolfs which are timed with the other mechanism to perform this function.

These and other objectives of the invention will be apparent to persons skilled in the art from a study of the foklllowing description and accompanying drawings in w ich:

FIG. 1 is a simplified elevational view showing the principal assemblies of the invention;

FIG. 2 is a fragmentary elevational view from the left of FIG. 1 showing the support structures;

FIG. 3 is a plan view of FIG. 1 with parts of the superstructure removed for clarity;

FIG. 4 is partial enlarged elevational view of a section of the container feed assembly;

FIG. 5 is a fragmentary plan view of FIG. 4 showing air pressure means for can transfer;

FIG. 6 is another fragmentary plan view of FIG. 4 showing the several stages of can transfer;

FIG. 7 is a partial plan view with parts broken away so that the power train and portions of the carriage adjustment may be traced;

FIG. 8 is a fragmentary sectional view showing the means to laterally adjust the two major assemblies with each other;

FIG. 9 is a fragmentary side view showing the power transfer to portions of the feed assembly;

FIG. 10 is a fragmentary view from the left of FIG. 9; d FIG. 11 is an enlarged elevational view of the spindle FIG. 11a is an inner face fragmentary elevational view of the takeolf disc;

FIG. 11b is a cross-sectional view along line 11b11b of 11a;

FIG. 12 is a sectional view of one of the individual spindles along the line 12l2 of FIG. 11;

FIG. 12a is a cross-sectional view along the ilne 12a 12a of FIG. 11;

FIG. 13 is a fragmentary elevational view of the throwout mechanism;

FIG. 14 is a view from the right of FIG. 13;

FIG. 15 is a sectional view of the solenoid stop for the hold out of the throw-out mechanism;

FIG. 16 is a sectional View along the line 1616 of FIG. 14;

FIG. 17 is a schematic view of the throw-out eccentric;

FIG. 18 is a fragmentary elevational view of a modified form of throw-out mechanism, but taken from the opposite side of the machine as compared with the throw-out mechanism shown in FIG. 13:

FIG. 19 is an end View of the mechanism shown in FIG. 18 and viewed from the right hand side;

FIG. 20 is a fragmentary cross-section taken on the line 202t) of FIG. 18;

FIG. 21 is a cross-section taken on the line 21-21 of FIG.. 18, and;

FIG. 22 is a horizontal cross-section of a modified form of spindle disc.

The general operation of the entire assembly may be understood by a reference to FIG. 1 where the major components of the apparatus are indicated. The machine is basically comprised of a can handling and feeding assembly 12 and a can printing assembly 14. Both assemblies are mounted on a common base 10. The printing assembly is fixedly secured to the base ill by the heavy frame member 16- While the printing assembly remains stationary with respect to base it the separately mounted feed assembly 12 is arranged so that it is capable of lateral and angular adjustment with respect to the printed assembly. This is accomplished by a three-tiered mounting consisting of a main base, a carriage, and a platform. The main base It is provided with tracks 22 (FIG. 2) which receive guide members 24 therein. Guide members 24 depend from a carriage 26. The track and guide members are anti-friction devices permitting the carriage 26 to readily reciprocate inwardly and outwardly with respect to the printing assembly 14. The controls and means for causing this reciprocation will be explained hereinbelow. Mounted on carriage 26 is a platform 28 which is pivoted about a vertical pin 29, whereby the platforms angular relationship and the superstructure supported thereby may be varied with respect to the can printing assembly 14. The vertical pin 29 is affixed to and extends upwardly from the secondary base or carriage 26.

A brief description of the path followed by the containers and of the operation of the major elements will facilitate an understanding of the details of the entire machine. Referring to FIG. 1, the cans C, which are to be printed, enter the machine via a pin carrying conveyor 3t). The cans are supported on pins 32 and transferred to a feed mechanism 31. From the feed mechanism they are further transferred to a constantly rotating star feed- Wheel 50 (see FIG. 4). The feed-wheel 50 receives the individual cans from the feed mechanism and delivers them to a second intermittent moving feed-wheel 54 at a point of transfer. Several stations later the can carrying pocket of star wheel 54 is disposed opposite an intermittently operated spindle disc iii. A feed cam 58 (seen best in FIGS. 1 and 4) contacts the cans C and forces them from the second star feed-wheel to one of the spindles 71 of disc 70. The drive mechanism is so arranged that the cam will rotate upon each instance of a can presentation by wheel 54, and a spindle presentation by disc 7t).

The spindle disc rotates in a counter-clockwise (as viewed in FIG. 1) direction and presents each can carrying spindle intermittently to engagement with a constantly rotating printing turret ltltl which is mounted in assembly 14-.

In the event there is no container on the spindle, or in the event there is an improperly seated one, means are provided to move that spindle out of an engagement with the printed cylinder, while permitting the very next cancarrying spindle to engage the cylinder.

The disc 7t) continues past the turret and presents the then printed cans to a take-off position opposite a clockwise rotating take-off disc 84. At the take-off positions, the cans are blown from the spindles onto suction cups, or the like, spaced about the inner surface one inch in from the periphery of the disc 84. The cans are again transferred from the take-off disc to pins 32 on conveyor chain 30 where they are subsequently taken to a drying oven.

The principal assemblies will now be discussed in detail.

T he can feed assembly For the purpose of this disclosure, the can feed assembly will be termed as that structure which transmits the cans from the conveyor 3% to the spindle disc '78.

The cans enter the system via the pin-carrying link chain 30. At a station prior to the instant printing station, the cans have been placed on the pins with their bottom (normally closed) ends adjacent the free or outer ends of their respective pins.

The path followed by the cans during this stage can best be seen by referring to FIGS. 4, 5 and 6. PEG. 4 shows most of the structure hidden from view by the plate 31 in FIG. 1. The chain 30 travels at any desired angle until changed into a gentle decline by sprocket gears 31 and 33. As the cans (and their pins 32) move along this gentle decline they come adjacent and parallel to a second conveyor 34 which is offset horizontally and vertically lower than chain 349. The conveyor chain 34 travels at the same speed as chain 36 and supports a plurality of elongated trough type can receivers 36 at identical spacings as pins 32 are spaced on chain 3d.

The pins and receivers are so coordinated that their paths will travel and mate vertically during their respective periods of horizontal travel.

FIGS. 5 and 6 disclose the horizontal relationships of the conveyors and their depending elements. As seen in FIG. 5 a conventional air pressure distribution block 453 has a plurality of air hoses 4148 to blow air-jets against the cans and thus transfer them from the support pins to the receivers 36.

The receivers 36 are elongated half-cylinders and have a closed end 37 which will act as a stop for the cans received therein. The plurality of air-jets are used, rather than a single ejection blast, so that over the horizontal length of travel the cans will have sufiicient time to be accurately positioned adjacent the ends 37 and remain there. This accurate positioning facilitates subsequent transfer operations.

As the can carrying receivers approach the end of their respective horizontal paths of travel, they are inverted as shown by the positions of receivers and 36b in FIG. 4. As the receivers are inverted by passing over a sprocket 35, they each deposit a can in one of four pockets of the counter-clockwise rotating star-wheel 5%. A guide 52 maintains the can in that particular pocket of the starwheel for a movement of approximately 270.

At the end of their arcuate travel the cans are removed from star wheel 56 by feed-wheel 54. The feed-wheel 5'4 has a dwell each time one of its pockets mesh with one of the pockets of star-wheel 50. The cans are lifted from the star-wheel 50 and intermittently travel another amount until they are presented to a dwell take-off station. This take-off station is opposite a point of dwell of the spindles on the spindle disc. The spindle disc has a dwell in its movement at the same instant as the star- Wheel 54. This is accomplished by gearing star-wheel 54 to the intermittently rotating spindle disc 7% in a manner to be described in detail hereinafter. A second guide 56 cooperates with the feed wheels to secure the cans therein until the take-off position, labeled 51, is reached.

Mounted adjacent the dwell or can take-oif position 51 is a constantly rotating cam 58 which is geared to starwheel 5t). As best seen in FIGS. 1 and 4, the cam rotates at each presentation of a can to the spindle disc. The cam design (FIG. 3) having a gentle taper 59 permits it to gently engage the bottom of each can by swiping across the bottom thereof and gradually, although swiftly, urging the can to the individual spindle member presented to the takeoff point Sit.

Spindle disc assembly The construction of the disc assembly can best be seen by referring to FIGS. 11 and 12. The rotatable disc 70 mates with a stationary plate, such as annular plate 76'. The plate 76 has a plurality of grooves or slots 64, 67, and St to which the interiors of the spindles will communicate in a manner to be described. The disc '76) and plate 79' provide a split construction permitting '70 to rotate relative to '70 and their mating surfaces have a sufi'iciently close tolerance so that sufiicient air pressures and vacuums can be maintained in the slots.

In some instances, cam 58 only partially seats the cans C on the spindle members 71 and for this reason auxiliary seating means are provided. These auxiliary seating means are a combination of a vacuum developed in the nose section of each spindle as it traverses its can take-on position, and a corresponding air blast 73 directed toward the spindle from a position slightly behind the cam. This last mentioned air blast is of most importance in handling cans not having closed bottoms where the spindle vacuum loses some of its effectiveness.

A cross-sectional view of an individual spindle is shown in FIGS. 12 and 12a. FIG. 12a shows the spindle as it traverses one of the slots, and FIG. 12 when it is not. Each spindle 71 has an interior channel 62 throughout its length. These channels are in communication with the slots 64, 6'7, and 80 behind the disc during various sectors of its circumferential travel. A vacuum in slot 64 is provided through conduits 68 in any conventional manner. Referring to FIG. 11, it can be seen that due to the arcuate length of slot 64, the vacuum in channel 62 is applied for a time and distance at and after the can take-on position 51. The channel 62 is enlarged or directed at the outer end of the spindle by an end plate shown by the numeral 63.

The outer surfaces of the spindles 71 are comprised of a hard plastic sleeve 73 which is mounted for free rotation on a fixed shaft 72 by bearings 74.

The cans have a free fit on the spindles but will frictionally rotate during printing with the sleeves 78 due to pressure applied by the printing cylinder. As the can engages the printing cylinder at point 76, the can (and spindle sleeve) will rotate through friction with the printing cylinder and be printed throughout its cylindrical surface. This is conventional and will be apparent to those skilled in the can-printing art.

This spindle disc continues in its intermittent counterclockwise rotation until position 77 where it receives a varnish overcoat and continues on until a take-off position 78 is reached. At position 78 the spindle disc is provided with another slot 3% which receives air pressure from conduit 82. As the channel 62 comes in communication with the slot St the can is ejected from the spindle onto a synchronized disc 84 which has means thereon (described below) to receive the cans and retransfer them to chain 3d during its upward vertical travel.

A front view of disc 84, mounted on the reverse side of plate 85, as seen in FIG. 4 is shown in FIG. 11a.

Disc 34 is also of split construction as is spindle disc 70. The disc 34 has a plurality of apertures 86 (FIG. 115) about the periphery of its surface facing the spindle disc 78. Spaced over each of these apertures, respectively, are a plurality of suction cups 558. On the surface opposite the suction cups is an annular plate 85 having ar-cuate grooves 89 and 91 which come in communication with the apertures as they move therepast.

The groove 89 is evacuated via conduit 89:; which provides suction for the cups at a point opposite where the cans are ejected from the spindle disc (i.e., opposite slot 78). The disc ti t is timed so that a suction cup is opposite a spindle each time a spindle is opposite slot 73.

Slot 91, which is under air pressure via tube 93, ejects the containers from the disc 34 into pins 31 as they move past. Since each of these elements are driven from a common drive, the synchronization of which will be apparent to those skilled in the art.

Sensing means Shown diagrammatically in FIG. 1 is a can-sensing device 29. This device may be any highly sensitive detecting device such as a sensitive spring connected to a micro-switch.

The leaf spring of the switch is positioned to rest just outside the ends of spindles 71 as they move past. If the cans are properly seated, no contact is made, if the can is not fully seated, the switch will be contacted 6 and the can blown off. It is very important that the cans be fully seated.

Working in cooperation with the micro-switch is an electric eye 21, shown diagrammatically on FIG. 1. The eye will determine the presence or absence of a can. The eye is adjusted so that the difference in light reflected from a can and that reflected from an empty spindle is discernible. One of the important functions of device 26, besides the prevention of improper printing is to ensure proper operation of the electric eye.

As mentioned heretofore, there is structure available to move the entire can handling assembly out of engagement with the printing assembly. The switches operated by the electric eye 21 activate this throw-out structure. The throw-out mechanism for accomplishing this will be explained in detail.

Switch 20, when activated, controls mechanism to eject the can from the spindle. Referring to FIG. 11, there is shown a conduit 9i for supplying air pressure to a slot 67 of the spindle disc. If the vacuum applied in space 64 does not seat the can properly because of a damaged can, the switch 20 controls apparatus to supply momentarily air pressure to space 67. The can will be ejected as the space 67 comes in communication with channel 62 of the spindle disc during its travel thercpast.

As the disc is rotated further the electric eye will detect this or any other no-can condition and the throw-out mechanism will be activated. In other words, if the switch 2 3 is activated, the switch 21 will always be activated; although switch 20 will not always be activated on each instance of switch 21 being activated. The importance of this will become apparent during a discussion of the throw-out mechanism.

Of course, if switch 20 is not tripped, only room pressure is in space 67. A conventional control to supply or shut off air to conduit 91) in response to switch 2% is well within the capabilities of a skilled worker.

An overcoat varnish attachment 2i), shown in dotted lines in FIG. 1, also has a similar throw-out mechanism.

T hr w-0ut mechanism As described earlier, in the event of a malfunction or no-can condition, all structure, including the can handling and feeding mechanism, which is mounted on carriage 25, will move into or out of engagement with the blanket cylinder. This is important because if the printing operation continues uninterrupted, printing ink will be applied to the plastic sleeves of the spindles 71 and each subsequent can placed on such a spindle will have its interior contaminated. t is also important that the spindles be promptly returned to engagement with the printing cylinder so that the high-speed operation may continue.

The throw-out mechanism for accomplishing this operation is disclosed in FIGS. 1347. The structure shown has as its objective, a slight rearward reciprocation of the mechanism supported by carriage 26 in rails 22, as the empty spindle traverses its normal printing area.

Referring now to FIG. 13, there is shown a standard 3%, fixedly secured to the base 10, and a framing member 391 (FIG. 14), rotatably supporting shaft 383 between them. The shaft is driven by the gear train which includes gears 293 and 315 The power is transferred via gear 316 so that the shaft 3% will rotate each time a can is presented to the printing cylinder. A box cam 305 is mounted on shaft 363 and is driven therewith. The box cam 3&5 is formed with an eccentric cam groove 304 about one surface which receives the cam follower 306.

The follower 3%, best observed in FIG. 13, is fastened to one end of link 3%. The link 3% has two additional cam followers, an intermediate cam follower 31d, and an ard 318 is comprised generally of an upright 322 and a box cam 324. The box cam 324 has a cam groove 326 which in its operating position receives cam follower 312. As viewed in FIG. 13, link 3% will oscillate about follower 312 as cam 3% follows the eccentricity of groove 3%.

An exteriorly contoured cam 328 (offset laterally from box earn 324) is also rotated by shaft 363. The cam is comprised of a generally circular surface 33% and a rise 332. The upright 322 has a cylindrical cam. follower 334 mounted intermediate its length. The follower 334 is positioned so that it is in slight tangential contact with rise 332 when the upright 322 is in its normal or operating position; that is, when cam follower 312 is received in groove 326 as shown in FIG. 13.

Along the upper surface of box cam 324 there is a detent 338. This detent receives a latch 349 which is controlled by the solenoid 342. The solenoid is under the control of the previously described electric eye 21 (FIG. 1) in a conventional manner. The latch 34%) maintains the standard 322 in the operating position even though it 322 is urged to the left (as seen in FIG. 13) by spring 344.

When the abnormal or no-can situation is sensed by eye 21, the latch 34th is withdrawn. The spring 344 will then urge and retain the standard 322 toward the cam 3-28. Cam follower 334 will permit the standard to move to the left as it leaves contact with surface 332 and engages surface 339 of the cam 328. This causes groove 326 to engage the middle cam follower 3H) and free the cam follower 312 of link 3558 for movement. The link 3% will now oscillate about follower 31.0 as a fulcrum as cam 366 follows the groove 304. This causes an up and down oscillating movement in follower 312. Follower 312 is also attached to an arm 349 which will follow its up and down movement.

It is this up and down oscillating movement of follower 312 which is utilized to move the can handling assembly out of engagement with the printing assembly.

The upright arm 349 connected to the follower 312 transfers the oscillating movement to a linkage system 35% which provides the connection between the can handling apparatus and the printing assembly. Basically the system converts this up and down motion to a lateral back and forth motion to move carriage 26.

The linkage system 359 is supported by the frame member 352 which is attached to base lit. The frame member has a removable split saddle member 354 at the upper end thereof. Rotatably mounted in said saddle is an eccentric 355 integrally or fixedly secured to an arm 356 which is connected to the arm 349.

Surrounding eccentric 355, is a steel eccentric strap 3%, which is connected to the carriage 26 (not shown) by a pivotal connection with member 361 as seen in FIG. 16. Since the strap closely engages the eccentric, and since the eccentric is pivoted about point ass, a pivotal movement about point 4% causes a longitudinal movement in arm 361.

Therefore, as arm 356 is lowered by member 349, the eccentric will move arm see to the right (as viewed in FIG. 13) and as a result the entire can handling assembly is moved to the right, which removes the empty spindle out of engagement with the printing cylinder.

The link 3439 and eccentric 356 will return when the cam 33d and followers 334 will allow it to, which returns the can handling assembly to printing position.

As cam 33%) rotates the rise 332 will again contact cam follower 334 and return arm 322 to (the right) its normal position, where latch 3 50 will again engage detent 338 to retain the arm until another no-can condition is sensed.

In actual position, it often occurs that the supply of cans for printing is exhausted for a period of time due to one reason or the other. At high speeds of operation, the constant reciprocating of carriage 25 is very undesirable. An important function of this invention is the means for overcoming this reciprocation.

This means includes a solenoid 372 supported on a strap 370 which extends rearwardly from the arm 356, as shown in FIGS. 15 and 16.

The solenoid arm 378 can be projected into, and retracted from, the vertically elongated slot 336. Also received in the slot is a cam follower 3% which is secured to the vertical arm 349 by a bolt 391. The eccentric arm 356 is loosely secured to arm 349 by a pin 357 which moves up and down in a slot 376. It will thus be seen that when the solenoid arm 378 is retracted (toward the left in FIG. 15) the arm 349 will have no effect on arm 3% because pin 357 will move loosely in slot 376 and follower 3% will move up and down in slot 380. During such movement, arm 349 is urged in an upward direction by spring 362.

When the solenoid arm 378 is projected into the slot above follower 3%, the movement of arm 349 will be transmitted to arm 356, and on the down stroke, the carriage 26 will be moved from its printing position and, conversely, when arm 34-9 is moved upwardly under the influence of cam link 3%, the carriage will be returned to printing position with arm 36f abutting against stop 392. When the enlarged portion 379 of the arm 378 is allowed to return to the enlarged portion of the slot, the pin 357 will ride up and down in the slot and not transmit motion to the linkage 35f During this up and down riding the spindles are held away from their printing position.

The solenoid 372 is controlled by a convenient counting device which can sense each missing can. The solenoid is then connected so that arm 375 will be withdrawn if, for instance, four succeeding spindles are Without cans. After the fourth signal is given, the arm 378 is withdrawn and the carriage 26 will remain in its retracted position until the machine again receives a supply of containers. this operation can also be performed by a conventional time delay device.

Adjustment mechanism For proper operation, and for flexibility of use, the distance and angular relationship between the printing cylinder and the individual spindles must be adjustable and capable of being accurately determined. For instance, a slight toe-in of the spindles with respect to the blanket cylinder is advisable because of spindle deflection due to its cantilever mounting. Since the blanket is constantly working against this toe-in, angular adjustment becomes important.

Likewise, when it is necessary to change spindles to accommodate a different size can, a longitudinal adjustment is necessary between the two major assemblies so that they will accurately mate with each other, and an appropriate toe-in adjustment must accompany this longi tudinal adjustment.

The angular adjustment is accomplished by pivoting platform 28 with respect to carriage 26. As previously mentioned the platform pivots about the pin 29 which pin is fixedly secured to the carriage and is directly in line with the driving gear. There is a fine adjustment lot) and locks 159 which secures the upper platform on the carriage when the adjustments are accomplished. There are a plurality of friction reducing bosses 154 spaced about the upper surface of carriage 26 upon which the platform rests. The weight of the assembly is normally enough to hold the platform in position, however conventional cam locking devices are also provided.

The power for the printer assembly is obtained from gear 2433 via the take-off gear 31% (FIG; 3). Gearing (not shown) associated with 2% is utilized to drive the inking units of assembly 14 directly in order that they will be coordinated with the can feeding apparatus.

The power for the can feeding mechanism is taken from gear 208 (FIG. 7) by way of idler 216, planetary gear 213, shaft 22?. and pinion 222.

At pinion 224 power is transferred to the can handling carriage. The pinion 224 mates with the pinion 222 

1. A MACHINE FOR DECORATING THE SURFACE OF CYLINDRICAL ARTICLES COMPRISING, A BASE, A REVOLVABLE PRINTING CYLINDER MOUNTED ON SAID BASE, A CAN FEED ASSEMBLY FOR PRESENTING SAID ARTICLES TO SAID CYLINDER AT A PRINTING STATION, A ROTATABLE DISC, A PLURALITY OF FREELY ROTATABLE ARTICLE CARRYING SPINDLES MOUNTED ON SAID DISC MEANS FOR ROTATING SAID DISC AND SAID CYLINDER FOR SEQUENTIALLY BRINGING SAID ARTICLE CARRYING SPINDLES INTO ROLLING ENGAGEMENT WITH SAID PRINTING CYLINDER, DETECTION MEANS FOR RECOGNIZING AN IMPROPERLY SEATED CONTAINER ON SAID SPINDLE, AND MEANS TO EJECT SAID CONTAINER FROM SAID SPINDLE IN RESPONSE TO A SIGNAL FROM SAID DETECTION MEANS. 